Note: Descriptions are shown in the official language in which they were submitted.
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"Articulated-arm transport system"
Description
The invention relates to a transport system for
transporting workpieces from a machining station into
the next machining station or intermediate store of a
press, press line, a simulator or the like.
Prior Art
Where the manufacture of a workpiece calls for a
plurality of work operations, such as cutting or
shaping, then for economic production the necessary
individual operations are carried out in a transfer
press or press line, as they are known. The number of
tools then corresponds to the number of work stages
which are necessary for the manufacture. In the presses
there are transport devices with which the workpieces
are transported from one workstation to the next.
In the case of transfer presses or large-component
transfer presses, the transport devices comprise
gripper or load bearing rails which extend through the
entire length of the shaping machine. In order to
transport the components, the load bearing rails are
fitted with gripper or holding elements. In this case,
a distinction is made, depending on the movement
sequence, between a two-axis transfer fitted with
suction crossmembers or a three-axis transfer fitted
with gripper elements. As an additional movement,
pivoting in- order to change the attitude of the
component during the transport step may be required.
This attitude change can also be carried out by an
orientation station arranged between the shaping
stages.
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The transfer movement is initiated via cams, which are
forcibly synchronized with the ram drive via movement
transmission elements. The manufacture of large-area
components, in particular, has led to the development
of large-component transfer presses of greater and
greater dimensions, based on the shaping force and the
transport paths. Tool spacings of the order of
magnitude of 5000 mm are entirely normal nowadays, and
therefore corresponding transport steps are also
necessary.
As a result of this development, the masses to be
accelerated and braked in the transfer systems are
completely opposed to the low masses of the components
to be transported. Since the transport step is to be
executed in an extremely short time, in order to
achieve the greatest possible number of press strokes
and therefore output of components, the system must
have a high speed and therefore also acceleration and
retardation.
A further disadvantage is the rigid movement sequence
which is predefined by the cam drives. The optimum
utilization of the free spaces between the lower and
upper tool during the ram stroke to transport the parts
is not possible.
In order to avoid these indicated disadvantages,
intellectual rights applications nowadays concern the
replacement of the previous transfer system by a
corresponding number of transfer systems arranged
between the machining stages and equipped with their
own drive. Such an arrangement is disclosed by
EP 0 672 480 Bi. Transfer systems arranged on the
uprights are equipped with a number of drives which, in
operative connection with the movement transmission
means, carry out the transport of the components. As a
special feature, the system can be re-equipped both as
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a two-axis transfer with suction beams and as a
three-axis transfer with grippers. However, this
universal use requires a corresponding outlay on
construction.
Likewise arranged in each upright area is a transfer
device disclosed by DE 196 544 75 Al. In this
application, elements which are known as - parallel
cinematics - are used for the drive. In a modification
of these known movement elements, however, telescopic
lengthening of the drive rods is not performed, but,
with a constant rod length, the attachment points are
changed and therefore the transport movements are
achieved. The attachment points that accommodate the
forces or torques are not constant in terms of their
distance from one another and, in particular when these
points are close to one another because of the desired
travel curve, support problems can occur. In order to
increase the stiffness of the system, further mutually
parallel links are also proposed, which are connected
to one another by transverse crossmembers. In order to
achieve functionally reliable transport of large-area
components, the proposed system becomes correspondingly
complicated and has a large overall height.
In DE 100 10 079, not previously published, the
applicant proposes a system having transport devices
arranged in the press upright area, which operate in a
way comparable with a pivoting-arm principle.
Crossmembers which are provided with component pick-up
and holding means and are arranged transversely with
respect to the transport direction are in each case
held and moved at their ends by these pivoting-arm
robots. Thus, the pivoting-arm robots are in each case
arranged in pairs and opposite each other in the
upright area. Because of the overall height and the
vertical movement required by the drive concept, the
transport system proposed is in particular suitable for
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presses with a relatively large overall height. The
pivoting arm comprises a rigid piece which results in a
correspondingly large pivoting radius. Since the
intention is for the workpieces to be removed at the
earliest possible time after the start of the ram
upward movement, the large pivoting radius and the
resulting obstructing edges are unfavorable. With this
system, a desirable flat entry or exit curve can be
implemented only with difficulty.
Object and Advantage of the Invention
The invention is based on the object of providing a
highly flexible and precise transport system with a low
overall height which ensures advantageous utilization
of the free movement between the upper and lower tool
for the purpose of insertion and -removal of workpieces.
The invention is based on the idea, instead of using a
rigid transport system, to design the. latter from two
parts which are connected to each other, mounted in an
articulated fashion. In order to achieve a flat entry
and exit curve, the pivoting angle of the first part
arm can be selected to appropriately large.
On the basis of the proposed design, in conjunction
with controlled drives, the pivoting angle can be
selected within any technically practical range. As a
result, in the tool area the transport arm is located
in a very flat attitude oriented toward the horizontal
plane.
~
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Thus, with a relatively small opening stroke of the
press ram bearing the upper tool, the articulated arm
can advantageously move into the clearance which forms
between the upper and lower tool.
Particularly advantageous is a design of the two
articulated arm parts with equal lengths, since then a
horizontal transport movement is executed. The suction
spider carrying the workpiece therefore carries out a
distortion-free horizontal movement. The vertical
movement necessary to deposit and raise the workpieces
is executed by a stationary lifting drive.
Given superimposition of the horizontal and the
vertical movements, an appropriately beneficial flat
curve course can be implemented at the start and end of
the transport movement. The large-component transfer
press or press line can be run without difficulty with
phase-shifted ram positions, which results in a
beneficial force distribution with a low drive power.
This measure likewise increases the component output by
reducing the transport times.
During the actual shaping operation, the
articulated-arm transport system should be located in a
lowered position in the upright area, as a result of
which beneficial accessibility to the rising ram is
provided for the following component transport. This
accessibility permits an early inward movement and, as
a result, in addition reduces the idle times. This
lowered parking position is also made possible by
superimposing the horizontal and the vertical
movements.
Depending on the task set, it may be necessary for the
attitude of the components to be changed between two
shaping stations. In a press line, the attitude change
takes place by means of intermediate stores,
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orientation stations as they are known. Since the
intermediate stores lead to an enlargement of the overall
press length, attempts are made to avoid this solution in
the case of large-component transfer presses. When used in
a large-component transfer press, if required, the
articulated-arm transportation system is designed with an
additional pivoting movement.
The installation position of the articulated-arm
transport system is any desired, that is to say the pivoting
movement can be carried out both above and below the
transport plane.
In accordance with this invention, there is
provided a device for transporting workpieces in a press,
pressline, large-component transfer press, or simulator, the
device comprising: a machining station having at least one
independent transport device for transporting the workpieces
and for carrying out two-axis transport movement, the at
least one transport device comprising: a pivoting arm, the
pivoting arm including first and second pivoting arm parts
mounted for movement in rotation, a first movement
transmission means coupled to the first pivoting arm part, a
drive motor for acting on the first movement transmission
means and controlling a magnitude of a pivoting angle of the
first pivoting arm part, a transverse crossmember having a
component holding means, a pick-up and bearing unit arranged
at one end of the second pivoting part for coupling the
transverse crossmember to the second arm part, linear
guides, a carriage coupled to the linear guides and mounting
at least the pivoting arm, a second transmission movement
means coupled to the carriage, and a stationary lifting
motor for vertically moving the carriage via the second
movement transmission means.
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Further details and advantages of the invention
emerge from the following description of exemplary
embodiments.
In the seven figures, in schematic form:
figure 1 shows a press line with an articulated-
arm transport system
figure 2 shows a large-component transfer press
with an articulated-arm transport system
figure 3a shows a detail of the articulated arm
drive
figure 3b shows an individual unit [sic] of
pivoting the transverse crossmember drive
figure 4 shows a plan view of figure 3a and
figure 3b
figure 5 shows a detail of pivoting the
articulated arm without a transverse crossmember
figure 6 shows a plan view of figure 5.
Description of the Exemplary Embodiments
By way of example, presses 2 and 3 from a press
line 1 are illustrated in figure 1. Press rams 4 and 5
carry upper tools 6 and 7. Lower tools 8 and 9 are located
on sliding tables 10 and 11. Arranged between the presses
are orientation stations 12 and 13. On the press
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uprights 14-17 there are the articulated-arm transport
systems 18-21 according to the invention, in different
functional positions. Vertical guide rails 22 are fixed
to the press uprights 14-17, carriages 23 with guides
24 carry the articulated arms 43, 44. The drive motor
for pivoting the arm is designated by 25. The
stationary lifting motor 26 for the vertical movement
is operatively connected via a gear 27 to a rack 28.
More detailed constructional details will be described
in following figures. The task of the articulated-arm
transport system 18-21 is to convey components
cyclically in the transport direction 29 through
machining and orientation stations arranged one after
another. The various movement sequences are not
illustrated chronologically but by way of example.
In order to load the first press 2, the component
holding means 31, for example suction spiders, fixed to
transverse crossmember 36 [sic] and belonging to the
articulated-arm transport system 18 pick up panels 32
from a panel stack 33. A shaped part 34 is removed from
the opened press 2 by the articulated-arm transport
system 19 and transported to the orientation station
12. Articulated-arm transport_ system 20 inserts a
component 35, which has previously experienced an
attitude change in the orientation station 12, into
press 3. Articulated-arm transport system 21 in turn
deposits a component 36 shaped in press 3 onto the
orientation station 13. The travel curve for the
component transport is identified by 37, that for the
parking position by 38. In this application, pivoting
of the components by the articulated-arm transport
system is not provided and, if required, is carried out
by the orientation stations 12, 13.
In each case the articulated-arm transport systems are
arranged on the press uprights in pairs and opposite
each other in mirror-image fashion. Pick-up elements
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for the transverse crossmember 30 carrying the
component holding means 31 are configured in such a way
that automatic replacement at a tool change is
possible.
The shaping of the articulated arm, which is
particularly beneficial in order to utilize the free
accessibility between the upper and lower tools, can
easily be seen. In addition, the travel curves 37, 38
clearly show the beneficial conditions for very flat
insertion and removal of the parts. Superimposition of
the vertical movement by means of the lifting drive 26
on the horizontal movement of the pivoting arm actuated
by the drive motor 25 results in very advantageous
movement sequences.
In addition, the proposed lowered parking position
benefits early insertion into the tool clearance.
Figure 2 shows the arrangement of an articulated-arm
transport system in a large-component transfer press
39. Illustrated by way of example are shaping stages in
different movement sequences. In order to reduce the
overall length of the press, intermediate stores or
orientation stations have been omitted. If a change in
the attitude of the component is necessary, this is
carried out directly by the articulated-arm transport
system. For this purpose, use is made of a drive 40,
which is connected via drive elements to the transverse
crossmember 30. The functional sequences are comparable
with those already described under figure 1.
Figure 3a and figure 3b show an articulated arm in
enlarged form in front view. For the purpose of
simplification and better clarification, the
illustration has been selected such that the drive
chain for the pivoting arm can be explained in figure
3a, and the drive for pivoting the transverse
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crossmember 30 can be explained in figure 3b. In
addition, reference is made to figure 4 for an
understanding of the function.
It is possible to see the vertical guide rails 22 and
the carriage 23, which can be moved in guides 24 and
carries the pivoting arm. The vertical movement is
effected by the stationary lifting motor 26, which
drives the gear 27 that is operatively connected to the
rack 28. In order to pivot the articulated arm,
according to figure 3a use is made of the drive motor
25, which drives gear 41. The gear 41 drives rack 42,
which is permanently connected to the first
pivoting-arm part 43. This connection effects the
pivoting movement of the first pivoting-arm part 43
about the axis of rotation 69. A further drive train is
used to pass on the pivoting movement from the first
pivoting-arm part 43 to the second pivoting-arm part
44. For this purpose, there is a first gear 45 in the
first pivoting-arm part 43. This gear 45 is permanently
connected to the carriage 23. The gear 46 meshes with
the gear 45, and the gear 47 meshes with said gear 46.
The gear 47 is permanently connected to the second
pivoting-arm part 44. If the pivoting movement of the
first pivoting-arm part 43 is initiated by the drive
motor 25 via gears 41, 42, then this movement produces
a rolling pivoting movement of the gears 46, 47 and, as
a result of the permanent connection to gear 47, the
corresponding pivoting of the second pivoting-arm part
44 about the axis of rotation 70.
The magnitude of the pivoting movement or the pivoting
angle 48 can be controlled continuously via the drive
25 which, for example, is designed as a controlled
servomotor. It is easy to see that the greater the
choice of pivoting angle 48, the more the
articulated-arm system 43, 44 approaches the horizontal
stretched attitude, and the smaller is the required
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clearance for the insertion or removal of the
components. A distortion-free horizontal movement is
achieved if, based on the axes of rotation or bearing
axes 67, 70, 62, the two pivoting-arm parts 43, 44 are
designed with the same length.
If a change in the attitude of the components during
the transport step is required as a further movement,
then this can be carried out in accordance with figure
3b. For this purpose, the pivoting drive 40 mounted on
carriage 23 drives the gear 49. Via intermediate gear
50, the rotational movement is transmitted to gear 51.
Gear 51 is connected to gear 53 via a common shaft 52.
Gear 53 drives the gear train 54-57 mounted in the
first pivoting-arm part 43. Gear 57 is permanently
connected, via a hollow shaft 58, to toothed belt
pulley 59 and drives the latter. Toothed belt pulley 59
drives toothed belt pulley 61 via toothed belt 60.
Toothed belt pulley 61 forms a unit with the pick-up
and bearing unit of the transverse crossmember 30 and
effects a pivoting movement about the pivot axis 62.
Since the pivoting drive 40 can also be a controlled
servomotor, a defined change in the attitude of the
components is ensured.
The pick-up and bearing unit for the transverse
crossmember 30 is designed, for example, as a cardan
joint 63, which also makes possible a horizontal and
vertical oblique position of the transverse crossmember
30. Elements for the automatic change of the transverse
crossmember 30 during a tool change are provided and
designated by 64.
The drive chains described in figures 3a and 3b can be
seen together from the sectional illustration of figure
4. In addition to other constructional details, it is
in particular possible to see the permanent connection
of gear 45 to carriage 23, required for the pivoting of
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the first pivoting-arm part 43, and likewise the
permanent connection of gear 47 to the second
pivoting-arm part 44. Since the opening angle between
the pivoting-arm parts 43, 44 is twice as great as that
of the pivoting angle 48, the transmission ratio from
gear 45 to gear 47 is accordingly also 2:1. The drive
chain hatched more darkly in figure 4 is used to pivot
the transverse crossmember 30 about the pivot axis 62.
An embodiment without pivoting the transverse
crossmember 30 is shown by figures 5 and 6. The
functional description of the vertical lifting movement
and the gear arrangement in the carriage 23 and the
first pivoting arm 43 can be taken from the previous
figures. In addition, the connection of the first
pivoting-arm part 43 to the second pivoting-arm part 44
via gear 47, and the moveable mounting of the arms is
constructionally identical to the embodiment already
described. New is the permanent connection of toothed
belt pulley 66 to the first pivoting-arm part 43. The
toothed belt drives 66, 67, 68 are now used to
stabilize the transverse crossmember 30 and hold it in
the correct attitude. The important factor here is
that, given the selected arrangement and geometry, the
belt pulley and therefore the transmission are
therefore selected in the ratio 2:1, that is to say the
belt pulley 68 has twice the diameter of the belt
pulley 66. Given equal lengths of the pivoting-arm
parts 44, 43, a satisfactory horizontal movement of
transverse crossmember 30 and component holding means
31 is thus again ensured.
The invention is not restricted to the exemplary
embodiments described and depicted. It also comprises
all configurations by persons skilled in the art within
the scope of the applicable claim 1. It is possible,
for example, to change the horizontal transport
movement into an oblique or diagonal movement. For this
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purpose, the gear 45 that is permanently connected to
the carriage 23 is driven via a further gear with drive
in such a way that a vertical movement is superimposed
on the horizontal movement.
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1 Press line
2 Press
3 Press
4 Press ram
Press ram
6 Upper tool
7 Upper tool
8 Lower tool
9 Lower tool
Sliding table
11 Sliding table
12 Orientation station
13 Orientation station
14 Press upright
Press upright
16 Press upright
17 Press upright
18 Articulated-arm transport system
19 Articulated-arm transport system
Articulated-arm transport system
21 Articulated-arm transport system
22 Vertical guide rails
23 Carriage
24 Guides
Drive motor
26 Lifting motor
27 Gear
28 Rack
29 Transport direction
Transverse crossmember
31 Component holding means
32 Panel
33 Panel stack
34 Component
Component
36 Component
37 Component transport travel curve
38 Parking position travel curve
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39 Large-component transfer press
40 Pivot drive
41 Gear
42 Gear
43 First pivoting-arm part
44 Second pivoting-arm part
45 Gear
46 Gear
47 Gear
48 Pivoting angle
49 Gear
50 Intermediate gear
51 Gear
52 Shaft
53 Gear
54 Gear
55 Gear
56 Gear
57 Gear
58 Hollow shaft
59 Toothed belt pulley
60 Toothed belt
61 Toothed belt pulley
62 Pivot axis
63 Cardan joint
64 Changing device
65 Mounting
66 Toothed belt pulley
67 Toothed belt
68 Toothed belt pulley
69 Axis of rotation
70 Axis of rotation
